Printing couple in a printing machine with a pivotable transfer cylinder

ABSTRACT

A printing couple in a printing machine is comprised of at least three cylinders, a forme cylinder, a transfer cylinder and a counter-pressure cylinder. The counter-pressure cylinder forms a printing location or point in cooperation with the transfer cylinder. The transfer cylinder is mounted in at least one lever which can be pivoted about an eccentrically pivoting axis in relation to the rotational axis of the forme cylinder. When the three cylinders are in a print position, a connecting plane through the axis of rotation of the forme cylinder and the pivoting axis of the lever forms an angle of between 25° and 65° with a plane through the axis of rotation of the cylinder forming the printing point.

The invention relates to a printing group of a printing press with apivotable transfer cylinder in accordance with the preambles of claims1, 2, 4, 5 or 8.

A printing group is known from DE 198 03 809 A1, whose forme cylinderhas one printing plate in the circumferential direction on itscircumference, and several printing plates in the longitudinaldirection. A transfer cylinder working together with the forme cylinderhas double the circumference and is embodied for having one printingblanket in the circumferential direction and two in the longitudinaldirection which, however, are arranged offset from each other in thecircumferential direction.

JP 10-071 694 discloses printing group cylinders with four groovesarranged next to each other and offset in the circumferential directionin respect to each other. The printing group cylinders have a so-calleddouble circumference.

An arrangement for a joint-free printing press is known from CH 345 906,wherein the joints of four dressings arranged next to each other ontransfer cylinders of double circumference, and the joints of fourdressings arranged next to each other on a forme cylinder, are arrangedoffset from each other.

A double printing group is known from DE 198 15 294 A1, wherein the axesof rotation of the printing group cylinders are arranged on one level.The cylinders have four times the width of a newspaper page (doublewidth) and a circumference of one height of a newspaper page. Thetransfer cylinders have endless sleeves, which can be laterallyexchanged through openings in the lateral wall.

Printing group cylinders of single circumference are known from U.S.Pat. No. 4,125,073, which have an oscillation damper. In the case ofwider printing presses, the forme cylinder has a double circumferenceand two printing plates arranged one behind the other. The grooves,which are arranged in the longitudinal direction next to each other andreceive the printing plates, are additionally offset in respect to eachother in the circumferential direction.

A double printing group is known from DE 44 15 711 A1 wherein, for thepurpose of improving the print quality, a plane which extendsperpendicularly to the paper web is inclined by approximately 0° to 10°in relation to a plane connecting the two axes of rotation of thetransfer cylinders.

JP 57-131 561 discloses a double printing group wherein the shafts ofthe printing group cylinders are arranged in one plane. The phases ofthe printing group cylinders are arranged with each other in such a waythat grooves for fastening the dressings roll off on each other, andsimultaneously on the two printing groups which are working together.

A double printing group is also disclosed in DE 34 12 812 C1 in whichthe cylinder shafts are arranged in a common plane, which extendsinclined in relation to the web to be imprinted. The placement of thetransfer cylinders against or away from other cylinders takes placealong an almost straight movement direction by means of double eccentriccams.

EP 0 862 999 A2 discloses a double printing group with two transfercylinders which are working together and are seated in eccentric, ordouble eccentric bushings, for the purpose of being placed against oraway from other cylinders. In another embodiment they are seated onlevers, which are seated eccentrically in respect to the forme cylindershaft and are pivotable.

A device for engaging or disengaging of a transfer cylinder of aprinting unit with cylinders which are arranged at angles in respect toeach other is known from DE 44 35 986 A1, wherein the transfer cylinderseated in a lever around the forme cylinder is initially placed againstthe forme cylinder by a first setting means via an eccentric device, andsubsequently against the counter-pressure cylinder by a second settingmeans acting on the lever. For adjusting purposes the lever iseccentrically seated on the journal of the forme cylinder.

A printing press with bridge-shaped printing units is known from EP 0741 013 A2 wherein the transfer cylinders seated in levers are pivotablearound the axis of rotation of the associated forme cylinder for formingan accessible spacing.

DE 44 02 389 A1 discloses for printing group cylinders located on onelevel, wherein the transfer cylinders are seated in pivotable levers.The disengagement of the cylinders from each other takes place bypivoting the forme cylinders, wherein one of the transfer cylinders isdisengaged from the cooperating transfer cylinder because of thepivoting away of the forme cylinder and because of gravity.

The object of the invention is based on creating a printing group of aprinting press with a pivotable transfer cylinder.

In accordance with the invention, this object is attained by means ofthe characteristics of claims 1, 2, 4, 5 or 8.

The advantages which can be gained by means of the invention lie inparticular in that a printing press is created by these means, which isconstructed in a compact, low-oscillating and rugged manner, provides alarge production variety and requires a comparatively low production andmaintenance outlay.

Minimizing the number of parts which must be designed to be movable fornormal operations and during setup, for example omitting the movement ofall cylinders, frame walls, bearings etc., assures a rugged andcost-effective construction.

The cylinders support each other by means of the linear arrangement ofthe printing group cylinders, i.e. the arrangement of the axes ofrotation of the printing group cylinders in the print-on position insubstantially one plane. This reduces the relative sagging of thecylinders. Even a compensation of the bending line (statically) of theforme and of the transfer cylinders in respect to each other can beachieved.

Since the dressings on the cylinders are not secured in groovesextending continuously over the length of the cylinders, but instead ingrooves which are offset in respect to each other in the circumferentialdirection, a groove beating in the course of the passage of the grooveduring the roll-off of two cylinders on each other is considerablyreduced. In an advantageous embodiment, in the case of two groovesarranged next to each other in the longitudinal direction, the groovesare arranged offset by 180° from each other.

The arrangement of the printing group cylinders and the grooves in sucha way that the grooves of each cylinder, which are offset in respect toeach other, roll off in the area of the opposite, offset groove of thecylinder working together with it, is particularly advantageous. Acompensation of the dynamic forces can occur in this way. At a fixedoffset angle of 180° and with a linear arrangement of the cylinders,destructive interference occurs at all production rates, i.e. angularspeeds, without an offset angle of the grooves needing to be changed asa function of the number of revolutions or the frequency.

The arrangement of printing group cylinders of single circumference isparticularly advantageous for printed products of a small and/orvariable number of pages and/or for print shops with restricted spaceavailability. In comparison with the production of the same product on aprinting press of double circumference (without assembling), no “double”plate change is required. In contrast to a printing press of doublecircumference, during assembling operations it becomes possible tocreate a page jump of two pages and in this way to produce increasedflexibility in the printed product.

The type of construction with all printing group cylinders of a singlecircumference permits a much more compact and easier construction incomparison with printing groups having one or several cylinders ofdouble circumference. Also, rubber blankets, which would have to bereplaced in case of damage, are smaller and therefore morecost-effective.

The use of printing blankets and printing plates makes it possible toseat the cylinders stably at both ends, which makes possible a simple,rugged and cost-effective construction of the frame receiving theprinting group cylinders.

Also, in view of a rugged and simple construction it is advantageous ifonly the transfer cylinders need to be moved for bringing the printinggroup into or out of contact with others. Although the forme cylinderscan be movably seated for adjusting the distance to the associatedtransfer cylinder as well as to a possible inking system and, ifprovided, a dampening system, the placement against or away from eachother of the transfer cylinders and the associated forme cylinders takesplace in an advantageous manner only by a movement of the transfercylinders.

The linear arrangement of the cylinders is made possible by means of aspecially selected movement in the area of the printing position, and atthe same time devices for movement into and out of contact, or movementsinto and out of contact of the forme cylinders are avoided. This, too,contributes to a rugged and simple construction.

For this purpose, in an advantageous embodiment the transfer cylindersare arranged in levers which are pivotably seated eccentrically inrespect to the forme cylinder axis. By means of the special placement ofthe pivot points and the size of the eccentric (in respect to the axisof rotation of the forme cylinder), together with the selectedinclination in respect to the plane of the cylinders constituting theprinting positions, or between the web and the plane of the cylinders, arapid disengagement from the associated cylinders, or the release of theweb is possible. The operational engagement and disengagement isperformed by means of the transfer cylinders alone, and in a preferredembodiment only by means of a setting movement.

In a possible variation, the transfer cylinders can be seated in doubleeccentric bushings which, at least in the area near the printingposition, makes possible an almost linear movement, which to a largeextent is perpendicular in relation to the plane of the cylinder axes.

The effective groove width is reduced by means of the dressings beingembodied in the form of so-called metallic printing blankets on thetransfer cylinders, because of which an excitation of oscillations isfurther reduced in an advantageous manner, and the non-printing area onthe cylinders, i.e. the “white edge” on the product, as well as paperwaste, are reduced.

An embodiment of the printing group with cylinders of singlecircumference, and the arrangement in one plane, with offset grooveswhich, however, alternatingly roll off on each other, and with dressingsembodied as metallic printing blankets on the transfer cylinders, isadvantageous in particular.

Cylinders, or rollers, of printing groups must be moved away from eachother out of an operating state “print on”, i.e. a print-on position,and back into contact with each other for washing, changing ofdressings, etc. in particular. The radial movement of the rollersrequired for this also contains a movement component in a tangentialdirection, whose size is a function of the structural design (levers, aswell as angles in respect to the nip point) of the setting device. If aspeed difference is created on the active jacket surfaces at the nippoint because of the displacement in relation to the operational state,this implies, because of the surface friction of the roller materialsused, a tangential frictional force component which is directed oppositethe setting movement. Therefore the setting movement is slowed by this,or its speed is limited. This is important in particular with printinggroup cylinders in case of so-called “windings”, since there largefrictional forces also result from the high pressures occurring.

It is therefore advantageous in a method for bringing cylinders into andout of contact with each other that a relative tangential speed in thearea near the contact, i.e. in the area of the nip point, of twocylinders or rollers working together, is reduced by the intentionalrotation, or turning, correlated with the movement, of at least one ofthe affected cylinders or rollers. Besides a reduction of the slowing ofthe displacement, an unnecessarily high load (friction, deformation) onthe dressings and/or the jacket surfaces of the involved cylinders orrollers is prevented.

Exemplary embodiments of the invention are represented in the drawingsand will be described in greater detail in what follows.

Shown are in:

FIG. 1, a schematic representation of a double printing group,

FIG. 2, a schematic representation of a three-cylinder offset printinggroup,

FIG. 3, a schematic representation of a double-wide double printinggroup,

FIG. 4, a schematic representation of a double-wide double printinggroup, highly symmetrical,

FIG. 5, a schematic representation of a linear double printing group ina section B-B in FIG. 1, with a curved setting track,

FIG. 6, a schematic representation of a non-linear double printing groupwith a curved setting track,

FIG. 7, a schematic representation of an H-printing group with a curvedsetting track,

FIG. 8, a lateral view of the seating of the cylinders,

FIG. 9, a section through the seating in FIG. 8,

FIG. 10, a portion of a device driving in pairs on the transfercylinder,

FIG. 11, a schematic front view in accordance with FIG. 10,

FIG. 12, a schematic front view of a double printing group withcylinders of differing circumference,

FIG. 13, the coverage of the forme cylinder with four newspaper pages,

FIG. 14, the coverage of the forme cylinder with eight tabloid pages,

FIG. 15, the coverage of the forme cylinder with sixteen vertical pagesin book format,

FIG. 16, the coverage of the forme cylinder with sixteen horizontalpages in book format.

A first printing group 01 of a printing press, in particular a rotaryprinting press, has a first cylinder 02, for example a forme cylinder02, and an associated second cylinder 03, for example a transfercylinder 03 (FIG. 1). Their axes of rotation R02, R03 define a plane Ein a print-on position AN.

On their circumferences, the forme cylinder 02 and the transfer cylinder03 have at least one interference in the circumferential direction onthe jacket surface, for example a disruption 04, 06 in the jacketsurface which is active during roll-off. This disruption 04, 06 can be ajoint between leading and a trailing ends of one or several dressings,which are arranged on the circumference, for example by means of amagnetic force or by material-to-material contact. However, asrepresented in what follows in the exemplary embodiments, these can alsobe grooves 04, 06, or slits 04, 06, which receive ends of dressings. Theinterferences, called grooves 04, 06 in what follows, are equivalentwith other interruptions 04, 06 on the active jacket surface, i.e. theoutward pointing face of the cylinders 02, 03 provided with dressings.

Each of the forme cylinders 02 and transfer cylinders 03 has at leasttwo grooves 04, 06 (or interruptions 03, 04, etc.). These two grooves04, 06 are respectively arranged one behind the other in thelongitudinal direction of the cylinders 02, 03, and offset in respect toeach other in the circumferential direction.

If the cylinders 02, 03 only have a length L02, L03, which substantiallycorresponds to two widths of a newspaper page, only two grooves 04, 06are provided, which are offset in respect to each other in thecircumferential direction and arranged one behind the other in thelongitudinal direction.

The grooves 04, 06 are arranged on the two cylinders 02, 03 in such away that, in the course of a rotation of the two cylinders 02, 03, theyroll off on respectively one of the grooves 06, 04 of the other cylinder03, 04. The offset of the grooves 04, 06 of each cylinder 02, 03 in thecircumferential direction is preferably approximately 180°. Therefore,after respectively one 180° rotation of the cylinders 02, 03, at leastone pair of grooves 04, 06 rolls off on each other, while on alongitudinal section a of the cylinders 02, 03, the cylinders 02, 03roll off unimpeded on each other.

The transfer cylinder 01 of the first printing group 01 forms a printingposition 09 together with a third cylinder 07 on a web 08, for example aweb 08 of material to be imprinted. This third cylinder 07 can beembodied as a second transfer cylinder 07 (FIG. 1), or as acounter-pressure cylinder 07 (FIG. 2), for example a steel cylinder orsatellite cylinder 07. In the print-on position AN, the axes of rotationR03 and R07 of the cylinders 03, 07 forming the printing position 09define a plane D (see FIG. 6).

In the embodiment of FIG. 5, in the print-on position AN the axes ofrotation R02, R03, R07 of the three cylinders 02, 03, 07 workingtogether are substantially located in a common plane E which in thiscase coincides with the plane D, and extend parallel with each other(see FIG. 5). If the satellite cylinder 07 has two printing positions onits circumference, a second printing group, not represented, ispreferably also arranged in the common plane E. However, it can alsodefine a plane E of its own, which is also different from the plane Dassociated with it.

As represented in the exemplary embodiment in FIG. 1, the third cylinder07 embodied as the second transfer cylinder 07 works together with afourth cylinder 11, in particular a second forme cylinder 11 with anaxis of rotation R11 and constitutes a second printing group 12. The twoprinting groups 01, 12 constitute a printing group 13, a so-calleddouble printing group 13, which imprints both sides of the web 08simultaneously.

In FIG. 5, during printing, i.e. in the print-on position AN, all axesof rotation R02, R03, R07, R11 of the four cylinders 02, 03, 07, 11 arelocated in the common plane E or D and extend parallel with each other.FIG. 6 shows a corresponding printing group 13, wherein respective pairsof forme and transfer cylinders 02, 03, 11, 07 form one plane E, and thetransfer cylinders 03, 07 form the plane D, which differs from the planeE.

In the case of the double printing group 13 (FIG. 1), the cylinders 07,11 of the second printing group 12 also have grooves 04, 06 with theproperties regarding the number and offset in respect to each otheralready described above in connection with the first printing group 01.Now the grooves 04, 06 of the four cylinders 02, 03, 07, 11 arepreferably arranged in such a way that respectively two grooves 04, 06of two cylinders 02, 03, 07, 11 which work together roll off on eachother.

In an advantageous embodiment, the forme cylinder 02 and the transfercylinder 03 each have a length L02, L03, which corresponds to four ormore widths of a printed page, for example a newspaper page, for example1,100 to 1,800 mm, in particular 1,500 to 1,700 mm, and a diameter D02,D03, for example 130 to 200 mm, in particular 145 to 185 mm, whosecircumference substantially corresponds to the length of a newspaperpage, “single circumference” (FIGS. 3 and 4) in what follows. The deviceis also advantageous for other circumferences, wherein the ratio betweenthe circumferences D02, D03 and the length L02, L03 of the cylinders 02,03 is less than or equal to 0.16, in particular less than 0.12, or evenless than or equal to 0.08.

In an advantageous embodiment each of the two cylinders 02, 03 has twogrooves 04, 06, each of which extends continuously at least over alength corresponding to two widths of a newspaper page (FIG. 3).

However, more than two grooves 04, 06 can be arranged per cylinder 02,03. In this case respectively two grooves 04, 06 arranged next to eachother can be arranged aligned, or respectively alternatingly. However,for example with four grooves 04, 06, the two grooves 04, 06 adjoiningthe front ends of the cylinders 02, 03 can be arranged in a commonalignment, and the two grooves 04, 06 located on the “inside” can bearranged in a common alignment, but offset in the circumferentialdirection in respect to the first mentioned ones (FIG. 4).

If the interruptions 04, 06 are actually embodied as grooves 04, 06, orslits 04, 06, the grooves 04, 06 schematically represented in FIGS. 1 to4 can be slightly longer than the width, or twice the width of theprinted page. In the circumferential direction they can also possiblyslightly overlap two grooves 04, 06 adjoining each other in thelongitudinal direction. This is not shown in such detail in FIGS. 1 to4, which are only schematic representations.

In view of the excitation, or damping of oscillations caused by groovebeating, it is particularly advantageous if the grooves 04, 06 on therespective cylinders 02, 03, 07, 11 are offset by 180° from each other.In this case the grooves 04, 06 between the forme cylinders 02, 11 andthe transfer cylinders 03, 07 of the two printing groups 01, 12 roll offsimultaneously and in the area of the same section in the longitudinaldirection of the cylinders 02, 03, 07, 11, in one stage of the cycle forexample on the same side, for example a side I (FIGS. 1, 3 and 4) of thedouble printing group 13, and in the other phase on a side II or, withmore than two grooves 04, 06 per cylinder 02, 03, 07, 11, for example inthe area of the center of the cylinders 02, 03, 07, 11.

The excitation of oscillations is considerably reduced by the offsetarrangement of the grooves 04, 06 and the roll-off of all grooves 04, 06in the described manner, and possibly also by the linear arrangement ofthe cylinders 02, 03, 07, 11 in one plane E. Because of the synchronous,and possibly symmetrical roll-off on the two printing groups 01, 12, adestructive interference with the excitation occurs which, with theselection of the offset by 180° of the grooves 04, 06 on the cylinders02, 03, 07, 11, takes place independently of the number of revolutionsof the cylinders 02, 03, 07, 11, or of the frequency.

If the interruptions 04, 06 are actually embodied as grooves 04, 06, inan advantageous embodiment they are embodied with a gap of little width,for example less than or equal to 3 mm, in the area of a jacket surfaceof the forme cylinders 02, 11, or of the transfer cylinders 03, 07,which gap receives ends of one or several dressings, for example one orseveral rubber blankets, on the transfer cylinder 03, 07, or ends of oneor several dressings, for example one or several printing plates, on theforme cylinders 02, 11. The dressing on the transfer cylinder 03, 07 ispreferably embodied as a so-called metallic printing blanket, which hasan ink-conducting layer on a metallic base plate. In the case of thetransfer cylinders 03, 07, the beveled edges are secured by clampingand/or bracing devices, for example, and in the case of forme cylinders02, 11 by clamping devices, in the grooves 04, 06.

A single, continuous clamping and/or bracing device can be arranged ineach one of the grooves 06 of the transfer cylinder 03 or—in case ofgrooves extending over several widths of newspaper pages—severalclamping and/or bracing devices can be arranged one behind the other inthe longitudinal direction. The grooves 04 of the forme cylinder 02, forexample, also have a single, or several clamping devices.

A “minigap technology” is preferably employed in the grooves 04 of theforme cylinders 02, 11, as well as in the grooves 06 of the transfercylinders 03, 07, wherein a leading end is inserted into a narrow groove04, 06 with an inclined extending suspension edge, the dressing is woundon the cylinders 02, 03, 07, 11, the trailing end is also pushed intothe groove 04, 06, and the ends are clamped, for example by means of arotatable spindle or a pneumatic device, to prevent them from slidingout.

However, it is also possible to arrange a groove 04, 06 embodied as anarrow slit 04, 06 without a clamping device for the dressing on theforme cylinders 02, 11, as well as for the dressing, embodied as ametallic printing blanket, of the transfer cylinders 03, 07, whichreceives the ends of the dressings. In this case the ends are secured inthe slit 04, 06 by their shaping and/or the geometry of the slit 04, 06.

For example, in an advantageous embodiment (FIG. 3), the transfercylinders 03, 07 have only two dressings, which are offset by 180° fromeach other in the circumferential direction, each of which has at leasta width corresponding to two widths of a newspaper page. In this casethe dressings, or the grooves 04 of the forme cylinders 02, 11, extendcomplementary thereto and must have either, as represented, twocontinuous grooves 04, each of the length of two widths of a newspaperpage, or grooves 04 which adjoin in pairs and are arranged aligned, eachof the length of two widths of a newspaper page. In the first case, inan advantageous embodiment each interruption 04 of the forme cylinder02, 11 actually embodied as a groove 04 has two clamping devices, eachof a length substantially corresponding to the width of a newspaperpage.

In an advantageous embodiment, the forme cylinders 02, 11 are coveredwith four flexible dressings, which adjoin each other in thelongitudinal direction of the forme cylinders 02, 11 and have a lengthin the circumferential direction slightly greater than the length of aprinted image of a newspaper page, and in the longitudinal directionhave a width of approximately one newspaper page. With the arrangementof continuous grooves 04 and only one clamping device per groove 04, 06,which has a length of two widths of a newspaper page, it is alsopossible to apply dressings of a width of two newspaper pages, so-calledpanoramic printing plates.

In connection with printing groups for which the need for a setup withpanoramic printing plates can be excluded, an arrangement can also be ofadvantage wherein the “outer” dressings which respectively adjoin theside I and the side II are aligned with each other, and the “inner”dressings are aligned with each other and are arranged offset by 180°from the first mentioned ones (FIG. 4). This highly symmetricalarrangement makes it additionally possible to minimize, or prevent, thedanger of an oscillation excitation in the plane E, which might resultfrom the non-simultaneous passage of the grooves 04, 06 on the sides Iand II. The alternating tensing and relaxation of the web 08 occurringalternatingly on the sides I and II, and oscillations of the web 08caused thereby, can also be avoided by this.

In a further development, the mentioned arrangement of the interruptions04, 06 on the respective cylinders 02, 03, 07, 11, as well as betweenthe cylinders 02, 03, 07, 11, and the possibly linear arrangement of thecylinders 02, 03, 07, 11, can be applied in particular to cylinders of alength L02, L03 substantially corresponding to six times the width of anewspaper page. However, in this case it can be advantageous to embodythe transfer cylinders 03, 07 and/or the forme cylinders 02, 11 with adiameter D02, D03 which results in a circumference which substantiallycorresponds to double the length of a newspaper page.

In an advantageous embodiment, for a mechanically simple and ruggedembodiment of the double printing group 13, the forme cylinders 02, 11are arranged fixed in respect to their axes of rotation R02, R11. Forbringing the printing groups 01, 12 in and out of contact, the transfercylinders 03, 07 are embodied to be movable in respect to their axes ofrotation R03, R07, and can be simultaneously moved away from theassociated forme cylinders 02, 11 and transfer cylinders 03, 07 workingtogether with them, or can be placed against them. In this embodimentonly the transfer cylinders 03, 07 are moved in the course of normaloperation of the printing press, while the forme cylinders 02, 11 remainin their fixed and possibly previously adjusted position. However, theforme cylinders 02, 11 can be seated in appropriate devices, for examplein eccentric or double eccentric bushings, in linear guide devices or onlevers, for adjustment.

As represented schematically in FIGS. 5 and 6, the transfer cylinders03, 07 can be movable along a curved setting track 17. The setting track17, as well as the transfer cylinders 03, 07 in a print-off position AB,are represented in dashed lines in FIG. 5.

One of the transfer cylinders 03 is seated, pivotable around a pivotaxis S, in a lever 18, schematically represented in FIG. 5. Here, thepivot axis S is located in the plane E, for example. In this case thelever 18 has a length between the seating of the axes of rotation R03,R07 of the transfer cylinders 03, 07 and the pivot axis S, which isgreater than the distance of the axes of rotation R03, R07 of thetransfer cylinders 03, 07 from the axes of rotation R02, R11 of theassociated forme cylinders 02, 11 in the print-on position AN. In thisway the simultaneous disengagement of the cooperating transfer cylinders03, 07 and the associated forme cylinders 02, 11 takes place, and forthe engagement the opposite.

However, as described in greater detail below, the pivot axis S can inparticular be arranged in a different way eccentrically in respect tothe axes of rotation R02, R11 of the associated forme cylinders 02, 11,for example at a distance from the plane E. Seating in a lever 18 takesplace preferably on the side I and the side II of the double printinggroup 13.

In a further exemplary embodiment, not represented, the setting track 17can be created by seating the transfer cylinders 03, 07 in eccentricbushings, in particular double eccentric bushing, not represented. It ispossible by means of double eccentric bushings to create a substantiallylinear setting track in the area of the print-on position AN, but in thearea remote from the printing position 09 a curved setting track 17, ifrequired, which permits a faster or greater movement out of contact ofthe transfer cylinders 03, 07 from the cooperating transfer cylinder 07,03 than from the assigned forme cylinders 02, 11, or vice versa. Seatingon side I and on side II of the double printing group 13 is alsoadvantageous for the employment of eccentric cams.

The course of the web 08 through the printing position 09, which is inthe print-on position AN, is also represented in FIGS. 5 and 6. Theplane E of the double printing group 13 (FIG. 5), or of the respectiveprinting group 01, 02 (FIGS. 5, 6), and the plane of the web 08intersect in an advantageous embodiment at an angle alpha of 70° to 85°.If the transfer cylinders 03, 07 have a circumference approximatelycorresponding to the length of one newspaper page, the angle alphashould be selected to be approximately 75° to 80°, for example,preferably approximately 77°, but if the transfer cylinders 03, 07 havea circumference approximately corresponding to two newspaper pages, theangle alpha should be selected to be approximately 80 to 85°, forexample, preferably approximately 83°. For one, this selection of theangle alpha takes into account the assured and rapid access to the web08 and/or the moving apart from each other of the transfer cylinders 03,07 over a minimized setting track 17, and also minimizes negativeeffects on the result of printing, which is decisively affected by theamount of a partial looping around the transfer cylinder(s) 03, 07(mackling, smearing).

At least one of the transfer cylinders 03, 07 can be advantageouslybrought out of contact sufficiently far so that, during printingoperations, the drawn-in web 08 can be moved through the printingposition 09 without touching it.

The double printing group 13 (here in a linear embodiment) can bemultiply employed, for example twice, as represented in FIG. 7, in aprinting unit 19, for example a so-called H-printing unit 19, in acommon lateral frame 20. In FIG. 7, a separate identification of therespective parts of the lower located double printing group 13, whichare identical to the upper double printing group 13, was omitted. Withan arrangement of all cylinders 02, 03, 07, 11 whose circumferencesubstantially corresponds to the length of a newspaper page, it ispossible to save structural space, i.e. a height h of the printing unit19. This of course also applies to individual printing groups 01, 12 fordouble printing groups 13, as well as for otherwise configured printingunits having several printing groups 01, 12. However, an improvedaccessibility of the cylinders 02, 03, 07, 11, for example for changingdressings, cleaning work and washing, maintenance, etc., can also be apriority in place of a savings in height h.

The print-on, or -off positions AN, AB have been drawn bold in alldrawing figures for the purpose of clarity. In FIG. 7, the transfercylinders 03, 07 are indicated in dashed lines in a second possibleposition along the setting track 17, wherein here, for example, theupper double printing group 13 is operated in the print-off AB position(solid lines), for example for a printing forme change, and the lowerdouble printing group 13 is operated in the print-on position AN (solidlines), for example for continued production.

In an advantageous embodiment, each one of the printing groups 01, 12has at least one drive motor 14 of its own for the rotatory driving ofthe cylinders 02, 03, 07, 11. The drive motor 14 is embodied as anelectric motor, in particular an asynchronous motor, synchronous motor,or as a dc motor.

In a schematically represented embodiment shown in FIG. 7, this can be asingle drive motor 14 for the respective printing group 01, 12 which, inan advantageous embodiment, in this case initially drives the formecylinders 02, 11, and power is transferred from there via a mechanicaldrive connection, for example spur wheels, toothed belts, etc., to thetransfer cylinders 03, 07. However, for reasons of space and for reasonsof the flow of moments, it can also be of advantage to transfer powerfrom the drive motor 14 to the transfer cylinders 03, 07, and from thereto the forme cylinders 02, 11.

In one embodiment a printing group 01, 12 has its own drive motor 14 percylinder 02, 03, 07, 11 (FIG. 7), which is mechanically independent ofthe remaining drive mechanisms and has a large degree of flexibility inthe various operating situations, such as production runs, registration,dressing changes, washing, web draw-in, etc.

For special requirements, for example for only one-sided imprinteroperations, or merely for the requirement for changing the relativeangle of rotation position of the forme cylinders 02, 11 in relation toeach other, driving is also possible wherein one of the forme cylinders02, 11 of a printing group 01, 12 has its own drive motor 14, and theremaining cylinders 02, 03, 07, 11 of the printing group 01, 12 have acommon drive motor 14.

The type of drive mechanism in FIG. 7 (top and bottom) is represented byway of example and can therefore be transferred to the respectivelyother printing groups 01, 12, or the other double printing group 13.

In an advantageous embodiment, driving by means of the drive motor 14takes place coaxially between the axes of rotation R02, R03, R07, R11and the motor shaft, if required with a coupling for compensating anglesand/or offset, explained in greater detail below. However, driving canalso take place via a pinion, in case the “moving along” of the motor14, or a flexible coupling between the drive motor and the cylinders 02,03, 07, 11, which are to be moved when required, is to be avoided.

If a drive motor 14 driving the transfer cylinder 03, 07 is to be takenalong in the course of the setting movement, in a further development itcan also be taken along on an appropriate guide device on the outside ofthe lateral frame 20, for example.

In further development of the exemplary embodiments it is advantageousif the inking system 21 assigned to the respective forme cylinders 02,11 and, if provided, the associated dampening unit 22, is rotationallydriven by a drive motor which is independent of the drive mechanism ofthe printing group cylinders. In particular, the inking system 21 andthe possibly provided dampening system 22 can each have their own drivemotors. In the case of an anilox inking system 21, the screen roller,and in connection with a roller inking system 21, for example, thefriction cylinder(s), can be rotationally driven individually or ingroups. Also, the friction cylinder(s) of a dampening system 22 can alsobe rotationally driven individually or in groups.

An exemplary embodiment for providing the linear curved setting track 17by means of the lever 18 is represented in FIGS. 8 and 9.

FIG. 8 shows a lateral view, in which only one of two journals 23 whichare arranged on the fronts of the transfer cylinders 03, 07 (in dashedlines) is visible. The lever 18 is seated, pivotable around the pivotaxis S, which is preferably fixed in place (but adjustable, if required)in respect to the lateral frame 20. In the embodiment represented, in aprint-on position AN, the axes of rotation R02, R03, R07, R11 of thecylinders 02, 03, 07, 11 shown in dashed lines, are again located in aplane E, which in this case coincides with the plane D between thecylinders 03, 07 which form printing positions 09.

The pivot axis S of the lever 18 is arranged eccentrically in respect tothe axes of rotation R02, R11 of the forme cylinders 02, 11 and islocated outside the plane E or D. Pivoting of the lever 18 around thepivot axis S by means of a drive mechanism 44, for example by means of apressure medium cylinder 44, via a setting means 46, for example asingle- or multi-part connector 46, for example a lever or toggle levermechanism 46, causes the transfer cylinders 03, 07 to be simultaneouslybrought out of and into contact with the assigned forme cylinders 02,11, or the respectively other transfer cylinders 07, 03. The togglelever mechanism 46 is hingedly connected with the lever 18 and with apivot point fixed on the frame. The advantageously double-actingpressure medium cylinder acts, for example, on a movable joint of thetoggle lever mechanism. The axes of rotation R02, R11 of the formecylinders 02, 11 remain at rest for this process. So that the movementof the two levers 18 per transfer cylinder 03, 07, which are arranged onthe front face, takes place synchronously, the setting means 44 can havea shaft 47, for example a synchronous shaft 47, which connects the twosetting means 44, or can be connected with such a one. To assure thedesired, for example linear, arrangement of the cylinders 02, 03, 07,11, a stop 48, which is preferably embodied to be adjustable, isprovided per lever 18.

The driving and setting means 44, 46 are designed and arranged in such away that the movement out of contact of the transfer cylinders 03, 07takes respectively place in the direction of the obtuse angle beta (fora straight web run 180°-alpha) between the web 08 and the plane D or E.

The eccentricity e-S of the pivot axis S in respect to the axes ofrotation R02, R11 of the forme cylinders 02, 11 lies between 7 and 15mm, in particular approximately 9 to 12 mm. In the contact position ofthe transfer cylinders 02, 03, 07, 11, i.e. the axes of rotation R03,R07 lie in the above mentioned plane D, the eccentricity e-S is orientedin such a way, that an angle epsilon-S between the plane D of thecylinders 03, 07 forming the printing position 09 and the connectingplane V of the pivot axis S and the axes of rotation R02, R11 liesbetween 25° and 65°, advantageously between 32° and 55°, in particularbetween 38° and 52°, wherein the pivot axis S lies preferably in thearea of an obtuse angle beta between the plane D and the incoming oroutgoing web 08, and is farther apart from the printing position 09 thanthe axes of rotation R02, R11 of the associated forme cylinders 02, 11.In case of a vertical and, except for a possible offset caused by thepartial looping around, straight path of the web, as well as an angle of77° between the plane D and the plane of the web 08, the eccentrics e-Shave an angle of, for example 12 to 52°, advantageously 19 to 42°, inparticular 25 to 39°, in respect to a horizontal line H.

In the ideal case, i.e. with never-changing conditions and atolerance-free production, the arrangement as described so far meets thedemands made on putting the printing groups 01, 12, or the doubleprinting group 13, into and out of contact without further settingmechanisms.

However, for compensating possibly occurring production tolerances,and/or for being able to perform a base positioning of the dressings,materials to be imprinted, etc., further actuating options for adjustingpurposes are provided.

The axes of rotation R02, R11 on the forme cylinders 02, 11 are seatedadjustably, for example also eccentrically in respect to their fasteningon the lateral frame 20, in this case in respect to a bore 49. In thepresent case, a journal 51 of the forme cylinders 02, 11 is arranged inan eccentric bearing 52, or an eccentric bearing bushing 52, which ispivotably seated in the bore 49.

A pivot axis S51 of the forme cylinders 02, 11 is eccentrically arrangedby an eccentricity of 5 to 15 mm, in particular approximately 7 to 12mm, in respect to the axes of rotation R02, R11 of the forme cylinders02, 11, and is located outside of the plane E.

In the contact position between the forme and the associated transfercylinders 02, 03, 07, 11, i.e. the axes of rotation R0, R03, or R11, R07are located in the plane E, the eccentricity e-S51 is oriented in such away that an angle epsilon-S51 between the plane E of the pair ofcylinders 02, 03, or 02, 11, and a connecting plane of the pivot axisS51 and the axes of rotation R02, R1 of the forme cylinders 02, 11 liesbetween 25° and 65°, advantageously between 32° and 55°, in particularbetween 38° and 52°. The pivot axis S5 is preferably located in a halfplane which is farther removed from the axes of rotation R03, R07 of theassociated transfer cylinders 03, 07 than the axes of rotation R02, R11of the associated forme cylinders 02, 11.

In the exemplary embodiment in accordance with FIG. 8, the pivot axisS51 for the eccentric seating of the forme cylinders 02, 11 coincideswith the pivot axis S of the lever 18.

The coincidence of the pivot axes S and S51 is not absolutely necessary,but practical. In particular, the pivot axis S, which is stationary inrespect to the lateral frame 20 and is not affected by the pivoting ofthe forme cylinders 02, 11, permits a simple and exact adjustment. Inprinciple, the lever 18 could also be arranged on an eccentric flange ofthe bearing bushing 52 which receives the journals 51, but duringturning this would result in a simultaneous displacement of thedistances between the forme cylinders 02, 11 and the transfer cylinders03, 07, as well as between the transfer cylinders 03, 07.

In an advantageous embodiment the two pivot axes S51 (and/or S) and S23of pairs of forme and transfer cylinders 02, 03, 11, 07 are arranged ontwo different sides of the plane E in the print-on position AN.

The position of the forme cylinders 02, 11 can be adjusted by means of asecond adjusting means 53 in accordance with the desired position inrespect to the plane E, or in regard to the required distance from thetransfer cylinders 03, 07 for the print-on position AN, by a slighttwisting of the eccentric bearing 52. After it has been adjusted, thisposition is set, for example, by not represented means.

For adjusting the printing gap at the printing position 09 into theprint-on position AN, at least the journals 23 of one of the twotransfer cylinders 03, 07, in this case the transfer cylinder 07, can beadjusted. For example, they are also eccentrically seated in theassigned lever 18. An eccentricity e-s23 of a pivot axis S23 in respectto the axes of rotation R03, R07 of the transfer cylinder lies between 1and 4 mm, in particular approximately at 2 mm. In the contact positionof the cylinders 03, 07 forming the printing position 09, i.e. the axesof rotation R03, R07 are located in the plane D, the eccentricity e-S23is oriented in such a way that an angle epsilon-S23 between the plane Dand the connecting plane of the pivot axis S23 and the axes of rotationR07 (R03) lies between 70° and 110°, advantageously between 80° and100°, in particular between 85° and 95°. In the example the angleepsilon-S23 should be approximately 90°.

An embodiment in accordance with FIG. 8 is represented in FIG. 9 in asection along the plane E. Each of the journals 51 of the formecylinders 02, 07 is rotatably seated in bearings 54, for example rollingbearings 54. In order to be able to provide a setting, or a correctionof the lateral register, this bearing 54, or an additional axialbearing, not represented, makes possible in an advantageous embodimentthe movement of the forme cylinders 02, 11, or their journals 51, in theaxial direction. The bearings 54 are arranged in the eccentric bearing52, or the eccentric bearing bushing 52, which in turn are arrangedpivotably in the bore 49 in the lateral frame 20. Besides the eccentricbearing bushing 52 and the bearing 54, further bearing rings andfriction bearings or rolling bearings can be arranged between the bore49 and the journals 51. The lever 18 is seated on a part of the bearingbushing 52 projecting from the lateral frame 20 in the direction towardthe forme cylinders 02, 11, and is pivotably seated in relation to it.On its end remote from the pivot axis S, the lever 18 receives thejournal 23 of the transfer cylinders 03, 07, which is arranged,rotatable in a bearing 56, and the latter, in the case of the transfercylinder 07, is arranged, pivotable around the pivot axis S-23, in aneccentric bearing 57, or in an eccentric bearing bushing 57. Ifrequired, a bearing bushing 57 which is pivotable in such a way can alsobe arranged for both transfer cylinders 03, 07.

The lateral frame 20 advantageously has recesses 58, at least on thedriven side of the printing press, in which the journals 23 of thetransfer cylinders 03, 07 can be pivoted. The setting means 46, 53, orthe drive means 44, are not represented in FIG. 8.

The rotatory drive of the cylinders 02, 03, 07, 11 is provided by meansof respectively individual drive motors 14, which are mechanicallyindependent from the drive mechanisms of the respectively othercylinders 02, 03, 07, 11 and are preferably arranged fixed in place onthe frame. The latter has the advantage that the drive motors 10 neednot be moved.

For compensating the pivot movement of the transfer cylinders 03, 07, acoupling 61, which compensates the angles and the offset, is arrangedbetween the transfer cylinders and the drive motor 10. It can embodiedas a double joint 61 or, in an advantageous embodiment can be embodiedas an all-metal coupling 61 with two torsionally rigid, but axiallydeformable multi-disk packets. The all-metal coupling can simultaneouslycompensate the offset and the position change caused by this. It isimportant that the rotatory movement be transmitted free of play.

Between the journal 51 and the drive motor 14, the drive mechanism ofthe forme cylinders 02, 11 also has a coupling 62, which absorbs atleast an axial relative movement between the cylinders 02, 11 and thedrive motor 14. For also being able to absorb production tolerances andpossibly required movements of the forme cylinders 02, 11 for adjustingpurposes, the coupling 62 is also embodied as a coupling 62 forcompensating at least minute angles and offsets. In an advantageousembodiment it is also embodied as an all-metal coupling 62, with twotorsionally rigid, but axially deformable multi-disk packets. The axialmovement is absorbed by means of multi-disk packets, which arepositively connected in the axial direction with the journal 51, or witha shaft of the drive motor 14.

For the case of of the cylinders 02, 03, 07, 11 being driven in pairs,schematically indicated in FIG. 6 in the lower double printing group 13,the forme cylinder 02, 11 is driven—for example via the attached gear 63or a pinion to a drive wheel of the forme cylinder 02, 11. Here theembodiment of cooperating drive wheels between the forme and transfercylinders 02, 03, 07, 11, each with spur toothing, is of advantage. Thelatter also applies for a pinion possibly arranged between the drivemotor 14 and the drive wheel of the forme cylinder 02, 11. An abovementioned individual encapsulation in this case extends around thepaired drive mechanisms of two cylinders 02, 03, 07, 11.

In a variation represented in FIGS. 10 and 11, a drive in pairs can alsotake place from the drive motor (if required via further gear elements,not represented) via a pinion 59 to a drive wheel 61 of the transfercylinders 03, 07, for example if it is intended to achieve a specialflow of moments.

In that case an axis of rotation R59 of the pinion 59 is arranged fixedon the frame in such a way that the straight line G1 determined by theaxis of rotation R59 of the pinion 59 and the pivot axis S of the lever18, together with a plane E18, determined by the pivot axis S of thelever 18 and the axes of rotation of the R03, R07 of the transfercylinders 03, 07, defines an opening angle eta in the range between +20°to −20°.

In a further development, a straight line G2 determined by the axes ofrotation R02, R11 of the forme cylinders 02, 11 and the axis of rotationR59 of the pinion 59, together with the straight line G1 determined bythe axis of rotation R59 of the pinion 59 and the pivot axis S of thelever 18, defines an opening angle lambda in the range between 160° and200°.

The above mentioned embodiments for driving, as well as for pivoting,the transfer cylinders 03, 07, and the embodiment of the lever 18 are tobe applied in the same way to printing groups in which the cylinders 02,03, 07, 11 do not all have the same circumference, or diameter (FIG.12). For example, the forme cylinder(s) 02, 11 can have a circumferenceU which has one printed page, for example the longitudinal page of anewspaper (“single circumference” in what follows). The cooperatingtransfer cylinders 03, 07 have, for example, a circumference ordiameter, which corresponds to a whole number multiple (greater than 1)of that of the forme cylinders 02, 11, i.e. it has a circumference, forexample, of two or even three printed pages of newspaper format (or iscorrespondingly matched to other formats).

If the printing position is constituted by a transfer cylinder 03, 07and a counter-pressure cylinder 07, 03, embodied as a satellite cylinder07, 03, the forme and the transfer cylinders 02, 11, 03, 07 can alsohave a single circumference, and the assigned counter-pressure cylinder07, 03 can be designed larger by a multiple.

An increased rigidity of the printing groups is also achieved in anadvantageous manner by means of the mentioned embodiments. This has aparticular advantage in connection with cylinders 02, 03, 07, 11 whichhave a length which corresponds to at least four, or even six, verticalprinted pages, in particular newspaper pages.

In contrast to printing presses with double circumference and singlewidth, the embodiment of the cylinders 02, 03, 07, 11 with double widthand—at least the forme cylinders 02, 11—with a “single circumference”makes a considerably greater product variability possible. Although themaximum number of possible printed pages remains the same, in the caseof single-width printing groups 01, 12 with double circumference theyare in two different “books”, or “booklets” in the assembly operation.In the present case with double-width printing groups 01, 12 of singlecircumference, the (double-width) webs 08 are longitudinally cut afterhaving been imprinted. In order to achieve a maximum booklet width, oneor several partial webs are conducted one above the other to theso-called folding superstructure, or turning deck, and are folded toform a booklet on a former without assembly operations. If such bookletthicknesses are not required, some partial webs can be guided on top ofeach other, but others can be conducted together to a second formerand/or folding apparatus. However, two products of identical thicknesscan also be conducted without being transferred to two foldingapparatus. A variable thickness of two different products is thusprovided. If, in case of a double folding apparatus or of two foldingapparatus, at least two product delivery devices are provided, it ispossible—depending on the arrangement—to conduct the two booklets, orproducts, next to or above each other to one side of the printing press,or to two different sides.

The double-width printing press of single circumference has a greatvariability, in particular when staggering the possible page numbers ofthe product, the co-called “page jump”. While the thickness per booklet(layer) in the printing press of double circumference and single widthcan only be varied in steps of four printed pages during assemblyoperation (i.e. with maximum product thickness), the describeddouble-width printing press of single circumference allows a “page jump”of two pages (for example when printing newspapers). The productthickness,. and in particular the “distribution” of the printed pages todifferent books of the total product or the products is considerablymore flexible.

Thus, after the web 08 has been longitudinally cut, the partial web isconducted either to a former and/or folding apparatus which is differentin respect to the corresponding partial web, or is turned to be alignedwith the last mentioned one. This means that in the second case thepartial web is brought into the correct longitudinal, or cuttingregister prior to, during or after turning, but before being broughttogether with the “straight ahead webs”. In an advantageous embodiment,this is taken into account as a function of the circumferentialdirection of grooves 04, 06, which are offset in respect to each other,of a cylinder 02, 03, 07, 11 by the appropriate design of the turningdeck (for example preset distances of the bars, or of the tracksections). Fine adjustment, or correction, is performed by means of thesetting tracks of the cutting register control device of the affectedpartial web and/or partial web strand, in order to place partial webs ontwo different running levels on top of each other with the correctregistration, when required.

Now, the forme cylinders 02, 11 can be provided in the circumferentialdirection with one vertical printed page in broadsheet format and in thelongitudinal direction with at least four (FIG. 13). Alternatively,these forme cylinders 02, 11 can also be selectively provided with twopages in the circumferential direction and, in the longitudinaldirection, with at least four horizontal printed pages in tabloid format(FIG. 14), or with two pages in the circumferential direction and, inthe longitudinal direction, with at least eight vertical printed pagesin book format (FIG. 15), or with four pages in the circumferentialdirection and in the longitudinal direction with at least fourhorizontal printed pages in book format (FIG. 16) by means ofrespectively one flexible printing plate which can be arranged in thecircumferential direction of the forme cylinder 03, and at least onearranged in its longitudinal direction.

Thus, depending on the coverage of the forme cylinders 02, 11 withhorizontal tabloid pages, or vertical newspaper pages, in particularbroadsheet pages, with horizontal or vertical book pages, it is possibleby means of the double-width printing press and at least the formecylinders 02, 11 of single circumference to produce different products,depending on the width of the web 08 used.

Thus, with the double printing group 13 the production, in one stage, oftwo vertical printed pages arranged on the forme cylinder (“two pagejump”) with variable products in broadsheet format, is possible.

With a width of the web 08 corresponding to four, or three, or twovertical printed pages, or of one vertical printed page in broadsheetformat, the production of a product in broadsheet format consisting of alayer in the above sequence with eight, or six, or four, or two printedpages is possible.

With a web width corresponding to four vertical printed pages inbroadsheet format, the double printing group can be used for producingrespectively two products in broadsheet format, consisting of one layerwith four printed pages in the one product and four printed pages in theother product, or with two printed pages in the one product and sixprinted pages in the other product. With a web width corresponding tothree vertical printed pages, it is suitable for producing respectivelytwo products in broadsheet format consisting of one layer with fourprinted pages in the one product and two printed pages in the otherproduct.

Furthermore, with a web width corresponding to four vertical printedpages in broadsheet format, the double printing group 13 can be used forthe production of a product in broadsheet format consisting of twolayers with four printed pages in the one layer and four printed pagesin the other layer, or two printed pages in the one layer and sixprinted pages in the other layer. With a web width corresponding tothree vertical printed pages, it can be used for producing a product inbroadsheet format consisting of two layers with four printed pages inthe one layer and two printed pages in the other layer.

In the case of printed pages in tabloid format, the double printinggroup can be used for producing in one stage printed pages arrangedhorizontally on the forme cylinder 02, 11 with variable products (“fourpage jump”) in tabloid format. Accordingly, with a web widthcorresponding to four, or three, or two horizontal printed pages, or toone horizontal printed page, the double printing group 13 can be usedfor producing a product in tabloid form consisting of one layer in theabove sequence with sixteen, or twelve, or eight, or four printed pages.

With a web width corresponding to four horizontal printed pages intabloid form, the double printing group can be used for producing twoproducts in tabloid format each consisting of one layer with eightprinted pages in the one product and eight printed pages in the otherproduct, or with four printed pages in the one product and twelveprinted pages in the other product. With a web width corresponding tothree horizontal printed pages, it can be used for producing twoproducts in tabloid format, each consisting of one layer with fourprinted pages in the one product and eight printed pages in the otherproduct.

With products in book format, the double printing group 13 can be usedfor producing in one stage eight printed pages with variable (“eightpage jump”) products arranged vertically on the printing cylinders 02,11.

With a web width corresponding to eight, or six, or four, or twovertical printed pages, the production of a product in book formatconsisting of a layer in the above sequence with thirty-two, ortwenty-four, or sixteen, or eight printed pages, is possible by means ofthe double printing group 13.

With a web width corresponding to eight vertical printed pages in bookformat, the double printing group 13 can be used for producingrespectively two products in book format, each consisting of one layer,with sixteen printed pages in the one product and sixteen printed pagesin the other product, or twenty-four printed pages in the one productand eight printed pages in the other product. With a web widthcorresponding to six vertical printed pages in book format, it can beused for producing respectively two products in book format, eachconsisting of one layer, with sixteen printed pages in the one productand eight printed pages in the other product.

For products in book format, the double-printing group 13 is furthermoreusable for producing, in one stage, eight printed pages arrangedvertically with variable products (“eight page jump”) on the formecylinder 03 (double transverse fold).

With a web width corresponding to four, or three, or two horizontalprinted products, or one horizontal printed page in book format, thedouble printing group 13 can be used for producing a product in bookformat consisting of a layer in the above sequence with thirty-two, ortwenty-four, or sixteen, or eight printed pages.

With a web width corresponding to four horizontal printed pages in bookformat, the double printing group can be used for producing respectivelytwo products in book format, each consisting of a layer, with sixteenprinted pages in the one product and sixteen printed pages in the otherproduct, or twenty-four printed pages in the one product and eightprinted pages in the other product. With a web width corresponding tothree horizontal printed pages in book format, it can be used forproducing respectively two products in book format, each consisting of alayer, with sixteen printed pages in the one product and eight printedpages in the other product.

If the two partial web strands are longitudinally folded on differentformers and thereafter conducted to a common folding apparatus, what wassaid above should be applied to the distribution of the products todifferent folded booklets, or layers, of the described variable numberof pages.

List of Reference Symbols

01 Printing group

02 Cylinder, forme cylinder

03 Cylinder, transfer cylinder

04 Interruption, groove, slit

05 -

06 Interruption, groove, slit

07 Cylinder, transfer cylinder, counter-pressure cylinder, satellitecylinder

08 Web, web of material to be imprinted

09 Printing position

10 -

11 Cylinder, forme cylinder

12 Printing group

13 Printing group, double printing group

14 Drive motor

15 -

16 -

17 Setting track, curved

18 Lever

19 Printing unit, H-printing unit

20 Lateral frame

21 Inking system, anilox printing system, roller printing system

22 Dampening system

23 Journal

44 Driving means, pressure medium cylinder

45 -

46 Setting means, coupling, toggle lever mechanism

47 Pivot point, shaft, synchronous shaft

48 Detent

49 Bore

50 -

51 Journal (02, 11)

52 Eccentric bearing, bearing bushing, eccentric

53 Setting means

54 Bearing, rolling bearing

55 -

56 Bearing

57 Eccentric bearing, bearing bushing, eccentric

58 Recess

59 Pinion

60 -

61 Drive wheel

E Plane

E18 Plane

D Plane

G1 Straight line

G2 Straight line

V Connecting plane

H Horizontal line

M Drive motor

S Pivot axis

S23 Pivot axis

S51 Pivot axis

U Circumference (02, 11)

AB Print-off position

AN Print-on position

a Longitudinal section

h Height

D02 Diameter

D03 Diameter

L02 Length (02)

L03 Length (03)

R02 Axis of rotation

R03 Axis of rotation

R07 Axis of rotation

R11 Axis of rotation

R59 Axis of rotation

I Side

II Side

alpha Angle

beta Angle

epsilon-S Angle

epsilon-S23 Angle

epsilon-S51 Angle

eta Angle (E18, G1)

lambda Angle (G1, G2)

1-37. (Cancelled) 38-147. (Not Entered)
 148. A printing group of aprinting press, having at least three cylinders (02, 03, 07, 11), namelya forme cylinder (02, 11), a transfer cylinder (03, 07) and acounter-pressure cylinder (07, 03), which forms a printing position (09)together with the transfer cylinder (03, 07), wherein for engagement ordisengagement the transfer cylinder (02, 03, 07, 11) is seated in atleast one pivotable lever (18), which is seated eccentrically in respectto an axis of rotation (R02, R11) of the forme cylinder (02, 11),characterized in that by means of the first adjusting device the formecylinder (02, 11) is seated to be movable in a direction perpendicularlyto its axis of rotation (R02, R11) in respect to a lateral frame (20),the lever (18) has a length between the seating of an axis of rotation(R03, R07) of the transfer cylinder (03, 07) and the pivot axis (S),which is greater than the distance of the axis of rotation (R03, R07) ofthe transfer cylinder (03, 07) from an axis of rotation (R02, R11) ofthe associated forme cylinders (02, 11) in the print-on position (AN),and that in the print-on position (AN) of the three cylinders (02, 03,07, 11), a connecting plane (V) through the axis of rotation (R02, R11)of the forme cylinder (02, 11) and the pivot axis (S) encloses an angle(epsilon-S) with a plane (D) through the axes of rotation (R03, R07) ofthe cylinders (03, 07) forming the printing position (09), which liesbetween 25° and 65°.
 149. A printing group of a printing press, havingat least three cylinders (02, 03, 07, 11), namely a forme cylinder (02,11), a transfer cylinder (03, 07) and a counter-pressure cylinder (07,03), whose axes of rotation (R02, R03, R07, R11) are located in aprint-on position (AN) of the cylinders (02, 03, 07, 11) in a comonplane (E), and wherein for engagement or disengagement the transfercylinder (02, 03, 07, 11) is seated in at least one lever (18), which ispivotable around a pivot axis (S), characterized in that the axis ofrotation (R02, R11) of the forme cylinder (02, 11) is fixedly seatedduring engagement or disengagement, and that, by pivoting the lever(18), only the transfer cylinder (03, 07) can be placed against or awayfrom the forme cylinder (02, 11) and from the counter-pressure cylinder(07, 03).
 150. The printing group in accordance with claim 149,characterized in that the lever (18) has a length between the seating ofan axis of rotation (R03, R07) of the transfer cylinder (03, 07) and thepivot axis (S), which is greater than the distance of the axis ofrotation (R03, R07) of the transfer cylinder (03, 07) from an axis ofrotation (R02, R11) of the associated forme cylinders (02, 11) in theprint-on position (AN).
 151. A printing group in accordance with claim148, characterized in that the pivot axis (S) of the lever (18)coincides with a pivot axis (S51) of an adjusting device of the formecylinder (02, 11).
 152. A printing group in accordance with claim 149,characterized in that the pivot axis (S) of the lever (18) coincideswith a pivot axis (S51) of an adjusting device of the forme cylinder(02, 11).
 153. The printing group in accordance with claim 148,characterized in that a first adjusting device is provided, by means ofwhich the distance between a rotary shaft (R012, R11) of the formecylinder (02, 11) and a rotary shaft (R03, R07) of the transfer cylindercan be set.
 154. The printing group in accordance with claim 149,characterized in that a first adjusting device is provided, by means ofwhich the distance between a rotary shaft (R012, R11) of the formecylinder (02, 11) and a rotary shaft (R03, R07) of the transfer cylindercan be set.
 155. The printing group in accordance with claim 148,characterized in that a second adjusting device is provided, by means ofwhich the distance between a rotary shaft (R03, R07) of the transfercylinder (03, 07) and a rotary shaft (R07, R03) of the counter-pressurecylinder (02, 11) can be set.
 156. The printing group in accordance withclaim 149, characterized in that a second adjusting device is provided,by means of which the distance between a rotary shaft (R03, R07) of thetransfer cylinder (03, 07) and a rotary shaft (R07, R03) of thecounter-pressure cylinder (02, 11) can be set.
 157. A printing group ofa printing press, having at least three cylinders (02, 03, 07, 11),namely a forme cylinder (02, 11), a transfer cylinder (03, 07) and acounter-pressure cylinder (07, 03), wherein for engagement anddisengagement the transfer cylinder (02, 03, 07, 11) is seated in atleast one lever (18), which is pivotable around a pivot axis (S), andwherein a first adjusting device is provided, by means of which thedistance between a rotary shaft (R02, R11) of the forme cylinder (02,11) and a rotary shaft (R03, R07) of the transfer cylinder can be set,characterized in that by means of the first adjusting device the formecylinder (02, 11) is seated to be movable in a direction perpendicularlyto its axis of rotation (R02, R11) in respect to a lateral frame (20),that a second adjusting device is provided, by means of which thedistance between a rotary shaft (R03, R07) of the transfer cylinder (03,07) and a rotary shaft (R07, R03) of the counter-pressure cylinder (02,11) can be set in that the transfer cylinder (02, 03, 07, 11) ispivotable seated in the lever (18) around a pivot axis (S23) which iseccentrically arranged in respect to its axis of rotation (R03, R07).158. The printing group in accordance with claim 148, characterized inthat the pivot axis (S) of the lever (18) coincides with a pivot axis(S51) of the first adjusting device.
 159. The printing group inaccordance with claim 157, characterized in that the pivot axis (S) ofthe lever (18) coincides with a pivot axis (S51) of the first adjustingdevice.
 160. The printing group in accordance with claim 157,characterized in that in the print-on position (AN) of the threecylinders (02, 03, 07, 11), a connecting plane through the axis ofrotation (R03, R07) of the transfer cylinders (03, 07) and the pivotaxis (S23) encloses an angle (epsilon-S23) with a plane (D) through theaxes of rotation (R03), R07) of the cylinders (03, 07) forming theprinting position (09), which lies between 70° and 110°.
 161. Theprinting group in accordance with claim 148, characterized in that adrive motor (14) for rotatory driving, which is mechanically independentfrom the other cylinder (02, 03, 07, 11), is assigned to each of theforme cylinders (02, 11) and the transfer cylinder (03, 07).
 162. Theprinting group in accordance with claim 149, characterized in that adrive motor (14) for rotatory driving, which is mechanically independentfrom the other cylinder (02, 03, 07, 11), is assigned to each of theforme cylinders (02, 11) and the transfer cylinder (03, 07).
 163. Theprinting group in accordance with claim 157, characterized in that adrive motor (14) for rotatory driving, which is mechanically independentfrom the other cylinder (02, 03, 07, 11), is assigned to each of theforme cylinders (02, 11) and the transfer cylinder (03, 07).
 164. Theprinting group in accordance with claim 148, characterized in that acommon drive motor (14) for rotatory driving, which drives the formecylinder (02, 11) or the transfer cylinder (03, 07), is assigned to thepair consisting of the forme cylinder (02, 11) and the transfer cylinder(03, 07).
 165. The printing group in accordance with claim 149,characterized in that a common drive motor (14) for rotatory driving,which drives the forme cylinder (02, 11) or the transfer cylinder (03,07), is assigned to the pair consisting of the forme cylinder (02, 11)and the transfer cylinder (03, 07).
 166. The printing group inaccordance with claim 157, characterized in that a common drive motor(14) for rotatory driving, which drives the forme cylinder (02, 11) orthe transfer cylinder (03, 07), is assigned to the pair consisting ofthe forme cylinder (02, 11) and the transfer cylinder (03, 07).
 167. Theprinting group in accordance with claim 161, characterized in that thedrive motor (14) driving the forme cylinder (02, 11) is arranged fixedon the frame.
 168. The printing group in accordance with claim 162,characterized in that the drive motor (14) driving the forme cylinder(02, 11) is arranged fixed on the frame.
 169. The printing group inaccordance with claim 163, characterized in that the drive motor (14)driving the forme cylinder (02, 11) is arranged fixed on the frame. 170.The printing group in accordance with claim 164, characterized in thatthe drive motor (14) driving the forme cylinder (02, 11) is arrangedfixed on the frame.
 171. The printing group in accordance with claim165, characterized in that the drive motor (14) driving the formecylinder (02, 11) is arranged fixed on the frame.
 172. The printinggroup in accordance with claim 166, characterized in that the drivemotor (14) driving the forme cylinder (02, 11) is arranged fixed on theframe.
 173. The printing group in accordance with claim 161,characterized in that the drive motor (14) driving the transfer cylinder(03, 07) is arranged fixed on the frame.
 174. The printing group inaccordance with claim 162, characterized in that the drive motor (14)driving the transfer cylinder (03, 07) is arranged fixed on the frame.175. The printing group in accordance with claim 163, characterized inthat the drive motor (14) driving the transfer cylinder (03, 07) isarranged fixed on the frame.
 176. The printing group in accordance withclaim 164, characterized in that the drive motor (14) driving thetransfer cylinder (03, 07) is arranged fixed on the frame.
 177. Theprinting group in accordance with claim 165, characterized in that thedrive motor (14) driving the transfer cylinder (03, 07) is arrangedfixed on the frame.
 178. The printing group in accordance with claim166, characterized in that the drive motor (14) driving the transfercylinder (03, 07) is arranged fixed on the frame.
 179. The printinggroup in accordance with claim 173, characterized in that a coupling(61), which compensates an angle and/or offset, is arranged between thedrive motor (14) and the transfer cylinder (03, 07).
 180. The printinggroup in accordance with claim 174, characterized in that a coupling(61), which compensates an angle and/or offset, is arranged between thedrive motor (14) and the transfer cylinder (03, 07).
 181. The printinggroup in accordance with claim 175, characterized in that a coupling(61), which compensates an angle and/or offset, is arranged between thedrive motor (14) and the transfer cylinder (03, 07).
 182. The printinggroup in accordance with claim 176, characterized in that a coupling(61), which compensates an angle and/or offset, is arranged between thedrive motor (14) and the transfer cylinder (03, 07).
 183. The printinggroup in accordance with claim 177, characterized in that a coupling(61), which compensates an angle and/or offset, is arranged between thedrive motor (14) and the transfer cylinder (03, 07).
 184. The printinggroup in accordance with claim 178, characterized in that a coupling(61), which compensates an angle and/or offset, is arranged between thedrive motor (14) and the transfer cylinder (03, 07).
 185. The printinggroup in accordance with claim 167, characterized in that the drivingconnection between the forme cylinder (03, 07) and the associated drivemotor (14) is embodied to absorb a relative movement between the formecylinder (02, 11) and the drive motor (14).
 186. The printing group inaccordance with claim 168, characterized in that the driving connectionbetween the forme cylinder (03, 07) and the associated drive motor (14)is embodied to absorb a relative movement between the forme cylinder(02, 11) and the drive motor (14).
 187. The printing group in accordancewith claim 169, characterized in that the driving connection between theforme cylinder (03, 07) and the associated drive motor (14) is embodiedto absorb a relative movement between the forme cylinder (02, 11) andthe drive motor (14).
 188. The printing group in accordance with claim170, characterized in that the driving connection between the formecylinder (03, 07) and the associated drive motor (14) is embodied toabsorb a relative movement between the forme cylinder (02, 11) and thedrive motor (14).
 189. The printing group in accordance with claim 171,characterized in that the driving connection between the forme cylinder(03, 07) and the associated drive motor (14) is embodied to absorb arelative movement between the forme cylinder (02, 11) and the drivemotor (14).
 190. The printing group in accordance with claim 172,characterized in that the driving connection between the forme cylinder(03, 07) and the associated drive motor (14) is embodied to absorb arelative movement between the forme cylinder (02, 11) and the drivemotor (14).
 191. The printing group in accordance with claim 153,characterized in that by means of the first adjusting device the formecylinder (02, 11) is seated to be movable in a direction perpendicularlyto its axis of rotation (R02, R11) in respect to a lateral frame (20).192. The printing group in accordance with claim 154, characterized inthat by means of the first adjusting device the forme cylinder (02, 11)is seated to be movable in a direction perpendicularly to its axis ofrotation (R02, R11) in respect to a lateral frame (20).
 193. Theprinting group in accordance with claim 157, characterized in that bymeans of the first adjusting device the forme cylinder (02, 11) isseated to be movable in a direction perpendicularly to its axis ofrotation (R02, R11) in respect to a lateral frame (20).
 194. Theprinting group in accordance with claim 191, characterized in that thefirst adjusting device has an eccentric bushing (52), which is seated inthe lateral frame (20) to be pivotable around a pivot axis (S51) andreceives a journal (51) of the forme cylinder (02, 11).
 195. Theprinting group in accordance with claim 192, characterized in that thefirst adjusting device has an eccentric bushing (52), which is seated inthe lateral frame (20) to be pivotable around a pivot axis (S51) andreceives a journal (51) of the forme cylinder (02, 11).
 196. Theprinting group in accordance with claim 193, characterized in that thefirst adjusting device has an eccentric bushing (52), which is seated inthe lateral frame (20) to be pivotable around a pivot axis (S51) andreceives a journal (51) of the forme cylinder (02, 11).
 197. Theprinting group in accordance with claim 194, characterized in that inthe print-on position (AN) of the forme cylinders and associatedtransfer cylinders (02, 03, 07, 11), a connecting plane through the axisof rotation (R02, R11) of the forme cylinder (02, 11) and the pivot axis(S) encloses an angle (epsilon-S51) with a plane (E) through the axes ofrotation (R02, R03, R07, R11) of the forme cylinders and associatedtransfer cylinders (02, 03, 07, 11), which lies between 25° and 65°.198. The printing group in accordance with claim 195, characterized inthat in the print-on position (AN) of the forme cylinders and associatedtransfer cylinders (02, 03, 07, 11), a connecting plane through the axisof rotation (R02, R11) of the forme cylinder (02, 11) and the pivot axis(S) encloses an angle (epsilon-S51) with a plane (E) through the axes ofrotation (R02, R03, R07, R11) of the forme cylinders and associatedtransfer cylinders (02, 03, 07, 11), which lies between 25° and 65°.199. The printing group in accordance with claim 196, characterized inthat in the print-on position (AN) of the forme cylinders and associatedtransfer cylinders (02, 03, 07, 11), a connecting plane through the axisof rotation (R02, R11) of the forme cylinder (02, 11) and the pivot axis(S) encloses an angle (epsilon-S51) with a plane (E) through the axes ofrotation (R02, R03, R07, R11) of the forme cylinders and associatedtransfer cylinders (02, 03, 07, 11), which lies between 25° and 65°.200. The printing group in accordance with claim 155, characterized inthat the transfer cylinder (03, 07) is seated movable in respect to thelever (18) in a direction perpendicular to its axes of rotation (R03,R07) by means of the second adjusting means.
 201. The printing group inaccordance with claim 156, characterized in that the transfer cylinder(03, 07) is seated movable in respect to the lever (18) in a directionperpendicular to its axes of rotation (R03, R07) by means of the secondadjusting means.
 202. The printing group in accordance with claim 157,characterized in that the transfer cylinder (03, 07) is seated movablein respect to the lever (18) in a direction perpendicular to its axes ofrotation (R03, R07) by means of the second adjusting means.
 203. Theprinting group in accordance with claim 200, characterized in that thesecond adjusting means has an eccentric bushing (57), which is seated,pivotable around a pivot axis (S23), in the lever (18) and receives ajournal (23) of the transfer cylinder (03, 07).
 204. The printing groupin accordance with claim 201, characterized in that the second adjustingmeans has an eccentric bushing (57), which is seated, pivotable around apivot axis (S23), in the lever (18) and receives a journal (23) of thetransfer cylinder (03, 07).
 205. The printing group in accordance withclaim 202, characterized in that the second adjusting means has aneccentric bushing (57), which is seated, pivotable around a pivot axis(S23), in the lever (18) and receives a journal (23) of the transfercylinder (03, 07).
 206. printing group in accordance with claim 203,characterized in that in the print-on position (AN) of at least theforme cylinder, the associated transfer cylinder and thecounter-pressure cylinder (02, 03, 07, 11), a connecting plane throughthe axis of rotation (R03, R07) of the transfer cylinder (03, 07) andthe pivot axis (S23) encloses an angle (epsilon-S23) with a plane (D)through the axes of rotation (R03, R07) of the cylinders (03, 07)forming the printing position (09), which lies between 70° and 110°.207. printing group in accordance with claim 204, characterized in thatin the print-on position (AN) of at least the forme cylinder, theassociated transfer cylinder and the counter-pressure cylinder (02, 03,07, 11), a connecting plane through the axis of rotation (R03, R07) ofthe transfer cylinder (03, 07) and the pivot axis (S23) encloses anangle (epsilon-S23) with a plane (D) through the axes of rotation (R03,R07) of the cylinders (03, 07) forming the printing position (09), whichlies between 70° and 110°.
 208. printing group in accordance with claim205, characterized in that in the print-on position (AN) of at least theforme cylinder, the associated transfer cylinder and thecounter-pressure cylinder (02, 03, 07, 11), a connecting plane throughthe axis of rotation (R03, R07) of the transfer cylinder (03, 07) andthe pivot axis (S23) encloses an angle (epsilon-S23) with a plane (D)through the axes of rotation (R03, R07) of the cylinders (03, 07)forming the printing position (09), which lies between 70° and 110°.209. The printing group in accordance with claim 148, characterized inthat the pivot axis (S) for the lever (18) is seated eccentrically inrespect to an axis of rotation (R02, R11) of the forme cylinder (02,11).
 210. The printing group in accordance with claim 149, characterizedin that the pivot axis (S) for the lever (18) is seated eccentrically inrespect to an axis of rotation (R02, R11) of the forme cylinder (02,11).
 211. The printing group in accordance with claim 157, characterizedin that the pivot axis (S) for the lever (18) is seated eccentrically inrespect to an axis of rotation (R02, R11) of the forme cylinder (02,11).
 212. The printing group in accordance with claim 148, characterizedin that the pivot axis (S) is arranged stationary in respect to alateral frame (20).
 213. The printing group in accordance with claim149, characterized in that the pivot axis (S) is arranged stationary inrespect to a lateral frame (20).
 214. The printing group in accordancewith claim 157, characterized in that the pivot axis (S) is arrangedstationary in respect to a lateral frame (20).
 215. The printing groupin accordance with claim 148, characterized in that an eccentricity(e-S) of the pivot axis (S) in respect to the axis of rotation (R02,R11) of the forme cylinder (02, 11) lies between 7 and 15 mm.
 216. Theprinting group in accordance with claim 209, characterized in that aneccentricity (e-S) of the pivot axis (S) in respect to the axis ofrotation (R02, R11) of the forme cylinder (02, 11) lies between 7 and 15mm.
 217. The printing group in accordance with claim 210, characterizedin that an eccentricity (e-S) of the pivot axis (S) in respect to theaxis of rotation (R02, R11) of the forme cylinder (02, 11) lies between7 and 15 mm.
 218. The printing group in accordance with claim 211,characterized in that an eccentricity (e-S) of the pivot axis (S) inrespect to the axis of rotation (R02, R11) of the forme cylinder (02,11) lies between 7 and 15 mm.
 219. The printing group in accordance withclaim 149, characterized in that in the print-on position (AN) of atleast the forme cylinder, the associated transfer cylinder and thecounter-pressure (02, 03, 07, 11), a connecting plane (V) through theaxis of rotation (R02, R11) of the forme cylinder (02, 11) and the pivotaxis (S) encloses an angle (epsilon-S) with a plane (D) through the axesof rotation (R03, R07) of the cylinders (03, 07) forming the printingposition (09), which lies between 30° and 60°.
 220. The printing groupin accordance with claim 157, characterized in that in the print-onposition (AN) of at least the forme cylinder, the associated transfercylinder and the counter-pressure (02, 03, 07, 11), a connecting plane(V) through the axis of rotation (R02, R11) of the forme cylinder (02,11) and the pivot axis (S) encloses an angle (epsilon-S) with a plane(D) through the axes of rotation (R03, R07) of the cylinders (03, 07)forming the printing position (09), which lies between 30° and 60°. 221.The printing group in accordance with claim 148, characterized in that aplane (E) of an axis of rotation (R02, R03 R07, R11) of at least oneforme cylinder and associated transfer cylinder (02,03, 07, 11) extendsinclines by an angle (alpha) of 75° to 85° in respect to the plane of aweb (08) passing through the printing group.
 222. The printing group inaccordance with claim 149, characterized in that a plane (E) of an axisof rotation (R02, R03 R07, R11) of at least one forme cylinder andassociated transfer cylinder (02,03, 07, 11) extends inclines by anangle (alpha) of 75° to 85° in respect to the plane of a web (08)passing through the printing group.
 223. The printing group inaccordance with claim 157, characterized in that a plane (E) of an axisof rotation (R02, R03 R07, R11) of at least one forme cylinder andassociated transfer cylinder (02,03, 07, 11) extends inclines by anangle (alpha) of 75° to 85° in respect to the plane of a web (08)passing through the printing group.
 224. The printing group inaccordance with claim 148, characterized in that during engagement ordisengagement the axis of rotation (R02, R11) of the forme cylinder (02,11) is seated fixed in a frame.
 225. The printing group in accordancewith claim 149, characterized in that during engagement or disengagementthe axis of rotation (R02, R11) of the forme cylinder (02, 11) is seatedfixed in a frame.
 226. The printing group in accordance with claim 153,characterized in that during engagement or disengagement the axis ofrotation (R02, R11) of the forme cylinder (02, 11) is seated fixed in aframe.
 227. The printing group in accordance with claim 154,characterized in that during engagement or disengagement the axis ofrotation (R02, R11) of the forme cylinder (02, 11) is seated fixed in aframe.
 228. The printing group in accordance with claim 157,characterized in that during engagement or disengagement the axis ofrotation (R02, R11) of the forme cylinder (02, 11) is seated fixed in aframe.
 229. The printing group in accordance with claim 148,characterized in that a print-on position (AN) of the cylinders (02, 03,07, 11), the axes of rotation (R02, R03, R07, R11) of the forme,transfer and counter-pressure cylinders (02,03, 07, 11) are located in acommon plane (E).
 230. The printing group in accordance with claim 149,characterized in that a print-on position (AN) of the cylinders (02, 03,07, 11), the axes of rotation (R02, R03, R07, R11) of the forme,transfer and counter-pressure cylinders (02,03, 07, 11) are located in acommon plane (E).
 231. The printing group in accordance with claim 157,characterized in that a print-on position (AN) of the cylinders (02, 03,07, 11), the axes of rotation (R02, R03, R07, R11) of the forme,transfer and counter-pressure cylinders (02,03, 07, 11) are located in acommon plane (E).
 232. The printing group in accordance with claim 148,characterized in that at least two of the cylinders (02, 03, 07, 11)have at least one axially extending interruption (04, 06) on theireffective jacket surfaces, which are arranged to alternatingly roll offon each other.
 233. The printing group in accordance with claim 149,characterized in that at least two of the cylinders (02, 03, 07, 11)have at least one axially extending interruption (04, 06) on theireffective jacket surfaces, which are arranged to alternatingly roll offon each other.
 234. The printing group in accordance with claim 157,characterized in that at least two of the cylinders (02, 03, 07, 11)have at least one axially extending interruption (04, 06) on theireffective jacket surfaces, which are arranged to alternatingly roll offon each other.
 235. The printing group in accordance with claim 148,characterized in that at least the forme and transfer cylinders (02, 03,07, 11) each have a circumference substantially corresponding to thelength of a section of a printed page in newspaper format.
 236. Theprinting group in accordance with claim 149, characterized in that atleast the forme and transfer cylinders (02, 03, 07, 11) each have acircumference substantially corresponding to the length of a section ofa printed page in newspaper format.
 237. The printing group inaccordance with claim 157, characterized in that at least the forme andtransfer cylinders (02, 03, 07, 11) each have a circumferencesubstantially corresponding to the length of a section of a printed pagein newspaper format.
 238. The printing group in accordance with claim148, characterized in that the forme cylinder (02, 11) has acircumference substantially corresponding to the length of a section ofa printed page in newspaper format, and the transfer cylinder (03, 07)has a circumference (U) corresponding to a whole number multiple notequal to one of the circumference of the associated forme cylinder (02,11).
 239. The printing group in accordance with claim 149, characterizedin that the forme cylinder (02, 11) has a circumference substantiallycorresponding to the length of a section of a printed page in newspaperformat, and the transfer cylinder (03, 07) has a circumference (U)corresponding to a whole number multiple not equal to one of thecircumference of the associated forme cylinder (02, 11).
 240. Theprinting group in accordance with claim 157, characterized in that theforme cylinder (02, 11) has a circumference substantially correspondingto the length of a section of a printed page in newspaper format, andthe transfer cylinder (03, 07) has a circumference (U) corresponding toa whole number multiple not equal to one of the circumference of theassociated forme cylinder (02, 11).
 241. The printing group inaccordance with claim 148, characterized in that in the area of theirbarrels the cylinders (02, 03, 07, 11) have a length (L02, L03) in thelongitudinal direction corresponding substantially to four widths of anewspaper page.
 242. The printing group in accordance with claim 149,characterized in that in the area of their barrels the cylinders (02,03, 07, 11) have a length (L02, L03) in the longitudinal directioncorresponding substantially to four widths of a newspaper page.
 243. Theprinting group in accordance with claim 157, characterized in that inthe area of their barrels the cylinders (02, 03, 07, 11) have a length(L02, L03) in the longitudinal direction corresponding substantially tofour widths of a newspaper page.
 244. The printing group in accordancewith claim 148, characterized in that at least two of the cylinders (02,03, 07, 11) each have at least two interruptions (04, 06) on theireffective jacket surface, which in the longitudinal direction of therespective cylinder (02, 03, 07, 11) are arranged next to each other,but in the circumferential direction are offset in respect to eachother.
 245. The printing group in accordance with claim 149,characterized in that at least two of the cylinders (02, 03, 07, 11)each have at least two interruptions (04, 06) on their effective jacketsurface, which in the longitudinal direction of the respective cylinder(02, 03, 07, 11) are arranged next to each other, but in thecircumferential direction are offset in respect to each other.
 246. Theprinting group in accordance with claim 157, characterized in that atleast two of the cylinders (02, 03, 07, 11) each have at least twointerruptions (04, 06) on their effective jacket surface, which in thelongitudinal direction of the respective cylinder (02, 03, 07, 11) arearranged next to each other, but in the circumferential direction areoffset in respect to each other.
 247. The printing group in accordancewith claim 148, characterized in that the counter-pressure cylinder (07,03) is embodied as a transfer cylinder (07, 03), to which a furtherforme cylinder (11, 02) is assigned.
 248. The printing group inaccordance with claim 149, characterized in that the counter-pressurecylinder (07, 03) is embodied as a transfer cylinder (07, 03), to whicha further forme cylinder (11, 02) is assigned.
 249. The printing groupin accordance with claim 157, characterized in that the counter-pressurecylinder (07, 03) is embodied as a transfer cylinder (07, 03), to whicha further forme cylinder (11, 02) is assigned.
 250. The printing groupin accordance with claim 244, characterized in that both transfercylinders (03, 07) are seated in pivotable levers (18).
 251. Theprinting group in accordance with claim 245, characterized in that bothtransfer cylinders (03, 07) are seated in pivotable levers (18). 252.The printing group in accordance with claim 246, characterized in thatboth transfer cylinders (03, 07) are seated in pivotable levers (18).253. The printing group in accordance with claim 148, characterized inthat at least two of the cooperating cylinders (02, 03, 07, 11) eachhave at least two interruptions (04, 06) on their effective jacketsurface, which in the longitudinal direction of the respective cylinder(02, 03, 07, 11) are arranged next to each other, but in thecircumferential direction are offset in respect to each other.
 254. Theprinting group in accordance with claim 149, characterized in that atleast two of the cooperating cylinders (02, 03, 07, 11) each have atleast two interruptions (04, 06) on their effective jacket surface,which in the longitudinal direction of the respective cylinder (02, 03,07, 11) are arranged next to each other, but in the circumferentialdirection are offset in respect to each other.
 255. The printing groupin accordance with claim 157, characterized in that at least two of thecooperating cylinders (02, 03, 07, 11) each have at least twointerruptions (04, 06) on their effective jacket surface, which in thelongitudinal direction of the respective cylinder (02, 03, 07, 11) arearranged next to each other, but in the circumferential direction areoffset in respect to each other.
 256. The printing group in accordancewith claim 253, characterized in that the interruptions (04, 06) on theeffective jacket surface of the cylinders (02, 03, 07, 11) are eacharranged to roll off in pairs on each other.
 257. The printing group inaccordance with claim 254, characterized in that the interruptions (04,06) on the effective jacket surface of the cylinders (02, 03, 07, 11)are each arranged to roll off in pairs on each other.
 258. The printinggroup in accordance with claim 255, characterized in that theinterruptions (04, 06) on the effective jacket surface of the cylinders(02, 03, 07, 11) are each arranged to roll off in pairs on each other.